US4725209A - Distributor type fuel injection pump - Google Patents

Distributor type fuel injection pump Download PDF

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Publication number
US4725209A
US4725209A US07/010,845 US1084587A US4725209A US 4725209 A US4725209 A US 4725209A US 1084587 A US1084587 A US 1084587A US 4725209 A US4725209 A US 4725209A
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US
United States
Prior art keywords
fuel
pressure chamber
chamber
shuttle piston
shuttle
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US07/010,845
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English (en)
Inventor
Akira Shibata
Shizuo Kawai
Yukinori Miyata
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Denso Corp
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NipponDenso Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by NipponDenso Co Ltd filed Critical NipponDenso Co Ltd
Assigned to NIPPONDENSO CO., LTD., A CORP. OF JAPAN reassignment NIPPONDENSO CO., LTD., A CORP. OF JAPAN ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: KAWAI, SHIZUO, SHIBATA, AKIRA, MIYATA, YUKINORI
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
    • F02M41/1411—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis characterised by means for varying fuel delivery or injection timing
    • F02M41/1422—Injection being effected by means of a free-piston displaced by the pressure of fuel

Definitions

  • the present invention relates to a distributor type fuel injection pump for distributing and supplying pressurized fuel to combustion chambers of an internal combustion engine and, more particularly, to an inner cam distributor type fuel injection pump, including a rotor which is rotatably driven, plungers disposed in the rotor to be slidable along the radial direction thereof, and a cam ring which is positioned to surround the rotor, and an inner surface of which is formed to be a cam surface to reciprocate the plungers along with rotation of the rotor, wherein fuel is drawn by reciprocation of the plungers in a pump chamber defined between the plungers, the fuel is pressurized, and then the pressurized fuel is distributed and supplied to each cylinder of the engine.
  • the inner cam type fuel injection pump is superior to the face cam type fuel injection pump in terms of high speed fuel injection and the rate of injection.
  • the fuel quantity introduced in the pump chamber defined between the above-mentioned plungers is controlled conventionally by a throttle mechanism.
  • the throttle mechanism has a throttle disposed in a passage which communicates the pump chamber with a supply source of fuel, and the size of an opening of the throttle can the pump chamber, i.e., the injection quantity of fuel varies in each injection stroke. Furthermore, since the viscosity of fuel changes in accordance with its temperature, it is difficult to control the injection be adjusted. Therefore, according to such a throttle mechanism, the quantity of fuel introduced into the pump chamber per stroke of the plungers, i.e., the injection quantity of fuel can be adjusted by changing the opening size of the throttle.
  • a distributor type fuel injection pump for distributing and supplying pressurized fuel to combustion chambers of an internal combustion engine, comprising: a rotor driven to be rotated; a pair of plungers reciprocated in a radial direction and coaxially with each other in the rotor, the plungers defining a pump chamber therebetween; a shuttle cylinder portion in which a cylinder bore is defined; a shuttle piston movably positioned in the cylinder bore and dividing the interior of the cylinder bore into first and second pressure chambers; connecting means for continuously connecting the pump chamber and the second pressure chamber; supply means for supplying the fuel into the pump chamber and the second pressure chamber through the connecting means and also supplying the fuel into the first pressure chamber, the fuel in the pump chamber and the second pressure chamber being pressurized when the pair of plungers are moved in a direction to reduce a volume of the pump chamber, and the fuel in the first pressure chamber being pressurized when the shuttle piston is moved by the pressure of the pressurized fuel in the second pressure chamber;
  • the injection quantity of fuel is determined by a moving distance of the shuttle piston from its initial to final positions.
  • the moving distance of the shuttle i.e., the injection quantity of fuel can be controlled in accordance with a drive condition of the engine.
  • FIG. 1 is a sectional view of a distributor type fuel injection pump according to a first embodiment of the present invention
  • FIG. 2 is a partially cut-away side view of fuel injection pump in FIG. 1;
  • FIG. 4 is an enlarged view of a part of fuel injection pump in FIG. 1;
  • FIG. 5 is a sectional view taken along the line V--V in FIG. 4;
  • FIG. 6 is a view for explaining a fuel system of the fuel injection pump in FIG. 1;
  • FIG. 7 is a sectional view taken along the line VII--VII in FIG. 6;
  • FIG. 8 is a sectional of a part of a distributor type fuel injection pump according to a second embodiment of the present invention.
  • FIG. 10 is a sectional view taken along the line X--X in FIG. 8.
  • a distributor type fuel injection pump as shown in FIGS. 1 to 3, has pump housing 1.
  • Drive shaft 2 is rotatably supported by one of the walls of housing 1.
  • Shaft 2 is rotated in synchronism with the crankshaft of the engine.
  • Shaft 2 is coupled to rotor 3 in housing 1.
  • Housing cover 4 is liquid-tightly mounted to an upper portion of housing 1.
  • Distribution head 5 is liquid-tightly mounted to another wall of housing 1 opposite to the wall and has head cylinder 6 therein.
  • Rotor 3 is concentrically and rotatably inserted in cylinder 6 and is coupled to shaft 2 to be rotated therewith.
  • Drive gear 11 is mounted to a portion of shaft 2 located inside housing 1.
  • Driven gear 12 is meshed with gear 11.
  • Gear 12 is mounted to main shaft 13 of the governor.
  • flyweights 15 are mounted to shaft 13 through holder 14.
  • governor sleeve 16 is moved in the axial direction of shaft 13 by the displacement of flyweights 15.
  • Sleeve 16 rotates a pivot lever in accordance with the rotational frequency of the engine as will be described later.
  • Feed passage 21 is formed in head 5, and fuel is supplied to passage 21 from a feed pump (not shown). Valve 22 for stopping the supply of fuel is provided to passage 21 (FIG. 2). Passage 21 communicates with regulate valve 23 (FIG. 3), and a pressure of fuel supplied to passage 21 is maintained at a constant pressure by valve 23.
  • Annular feed groove 24 is formed in head 5 to surround cylinder 6, and groove 24 communicates with passage 21.
  • first and second supply holes 25 and 26 are formed in cylinder 6 and are spaced apart from each other along the axial direction of cylinder 6. Radial inner ends of holes 25 and 26 are respectively opened to the inner surface of cylinder 6 in which rotor 3 is inserted. Radial outer ends of holes 25 and 26 communicate with groove 24 and passage 21, respectively.
  • First and second inlet ports 27 and 28 are respectively formed on the outer surface of rotor 3 and spaced apart from each other along the axial direction of rotor 3.
  • First and second inlet ports 27 and 28 can be connected to holes 25 and 26.
  • Ports 27 and 28 are provided in a number equal to the number of cylinders of the engine and disposed at equal intervals along the circumference of rotor 3 (FIG. 6).
  • Ports 27 and 28 are sequentially communicated with corresponding holes 25 and 26 during rotation of rotor 3. In this case, one of ports 27 communicates with hole 25 and at the same time, one of ports 28 communicates with hole 26.
  • Each of ports 27 and 28 is formed as a groove parallel to the axis of rotor 3.
  • ports 27 and 28 communicate with annular grooves 29 and 30 formed on the outer surface of rotor 3, respectively.
  • Grooves 29 and 30 are communicated with fuel supply passage 33 and pumping passage 34 formed in rotor 3, respectively through communication passages 31 and 32.
  • Supply passage 33 and pumping passage 34 are arranged concentrically with respect to the axis of rotor 3 and independently from each other.
  • Passages 33 and 34 are axially provided from both end surfaces of rotor 3, and opened ends of passages 33 and 34 are closed liquid-tightly by plugs 35 and 36, respectively.
  • Cam ring 40 is located adjacent to the inner end of head 5 and, although not shown in detail, supported to be rotatable about the axis of rotor 3 with respect to the inner surface of housing 1.
  • wave-shaped cam surface 41 is formed circumferentially on the inner surface of cam ring 40.
  • Cam ridges of surface 41 are formed in a number equal to the number of the cylinders of the engine and disposed circumferentially at equal intervals.
  • Cylinder bore 43 extends diametrically through the projected end of rotor 3 surrounded by ring 40, and a pair of plungers 42 are inserted in bore 43.
  • the outer end of each plunger 42 is coupled to a roller shoe slidably inserted in bore 43, like plunger 42.
  • Each roller shoe rotatably holds cam roller 44, and each cam roller rotatably contacts surface 41 of cam ring 40.
  • cam ring 40 is coupled to pin 45, as shown in FIG. 1, and pin 45 is coupled to timer piston 46.
  • Piston 46 is slidably fitted in timer cylinder bore 47 formed in housing 1. As is apparent from FIG. 1, the axis of bore 47 is perpendicular to that of cam ring 40.
  • cam ring 40 is rotated about its axis, and the position of the phase angle of surface 41 is circumferentially displaced, so that the timing of the pump action by reciprocation of plungers 42 is advanced or delayed. Accordingly, the injection timing of fuel can be controlled.
  • distribution hole 50 which communicates with passage 33 is formed in the other end portion of rotor 3, i.e., a portion where passage 33 is formed.
  • Hole 50 is connected to distribution port 50a opened on the outer surface of rotor 3.
  • delivery holes 51 can be connected to port 50a and are formed in the same number as that of cylinders of the engine. Holes 51 are distributed radially and uniformly in cylinder 6.
  • Port 50a sequentially communicates with respective holdes 51 along with the rotation of rotor 3. In this case, when ports 27 and 28 and corresponding holes 25 and 26 are disconnected, port 50a communicates with one of holes 51.
  • ports 27 and 28 are connected to holes 25 and 26 when port 50a is connected to hole 51, for drawing convenience.
  • Each hole 51 is connected to each combustion chamber of the engine through delivery passage 52 and delivery valve 53 disposed in passage 52.
  • shuttle mechanism 60 is provided to head 5. Mechanism 60 will be described below.
  • Shuttle cylinder 61 is arranged in head 5 in a direction perpendicular to the axis of rotor 3. As shown in FIG. 5, cylinder bore 62 is formed in cylinder 61 on the axis perpendicular to the axis of rotor 3.
  • Shuttle piston 63 is slidably fitted in bore 62 to divide it into first and second pressure chambers 62a and 62b. Volumes of chambers 62a and 62b are changed by the axial motion of piston 63.
  • Chamber 62a is defined between an end surface of piston 63 and plug 64 liquid-tightly inserted in bore 62
  • chamber 62b is defined between the other end surface of piston 63 and control rod 65 inserted in cylinder 61 to be perpendicular to the axis of piston 63.
  • Rod 65 is liquid-tightly fitted in hole 75 formed in cylinder 61 to be movable along its axis and rotatable thereabout.
  • Cam surface 66 is provided on the outer surface of rod 65 and defined by a bottom surface of a groove formed in the outer surface of rod 65, as shown in FIG. 5.
  • the depth of surface 66 i.e., the bottom surface of the groove, is gradually changed along the axis of rod 65, and is, as shown in FIG. 7, changed circumferentially with respect to rod 65.
  • the other end surface of piston 63 i.e., pin 63a projecting from piston 63, slidably abuts against surface 66 having the above-mentioned profile.
  • the distal end of pin 63a is formed to be round. Piston 63 is urged against rod 65 by spring 67 housed in chamber 62a.
  • Chambers 62a and 62b of mechanism 60 are connected to grooves 29 and 30 formed in rotor 3, respectively, through fuel passages 68 and 69 formed in cylinder 61 and head 5. Accordingly, chambers 62a and 62b always communicate with passages 33 and 34, respectively.
  • spill hole 71 is formed in cylinder 61. Hole 71 is closed by the outer surface of piston 63 in a state shown in FIG. 5. When piston 63 is moved from the state shown in FIG. 5 along a direction to reduce the volume of chamber 62a, hole 71 is opened by spill lead 70 formed by a step surface of piston 63 and thus connected to chamber 62b.
  • hole 71 communicates with annular groove 72 formed in the outer surface of cylinder 61 and is connected to passage 73 or fuel tank (not shown) through annular groove 72 and spill passage 73 (schematically shown in FIG. 6).
  • the upper end of rod 65 projects from the upper surface of head 5 and, as shown in FIGS. 1 and 3, is connected to pivot lever 90 and full load shaft 91, respectively.
  • Lever 90 is mounted to support shaft 92 rotatably projecting from the upper surface of head 5, as shown in FIG. 3, and is pivoted about shaft 92 along with the motion of sleeve 16 described above.
  • shaft 92 together with lever 90 are pivoted by the motion of sleeve 16
  • the rotation of shaft 92 is transferred to rod 65 so that rod 65 is rotated about its axis.
  • lever 90 is biased by spring 93 to abut against sleeve 16.
  • the biasing force of spring 93 can be adjusted by shaft 94.
  • Shaft 91 is rotatably mounted to housing 1 and coupled to, e.g., an accelerator pedal of an automobile through a coupling mechanism (not shown). Therefore, shaft 91 can be rotated in accordance with a depressed amount of the accelerator pedal. By rotation of shaft 91, rod 65 can be displaced along its axis. It should be noted that spring 95, shown in FIG. 5, serves to return rod 65 to a predetermined position along its axis, i.e., an initial position.
  • An operation of fuel injection pump of the first embodiment is as follows.
  • distribution port 50a is not connected to any of delivery holes 51, i.e., port 50a is closed.
  • fuel from feed passage 21 is supplied to fuel supply passage 33 and pumping passage 34 through one of holes 25 and 26 and a corresponding one of ports 27 and 28, and through annular grooves 29 and 30 and communication passages 31 and 32.
  • Passages 33 and 34 communicate with first and second pressure chambers 62a and 62b of shuttle mechanism 60 through fuel passages 68 and 69, respectively.
  • the fuel is also supplied to chambers 62a and 62b.
  • shuttle piston 63 is subjected to the force of spring 67 and urged against control rod 65.
  • spill hole 71 is closed by spill lead 70 of piston 63, and pin 63a of piston 63 abuts against cam surface 66 of rod 65.
  • passages 33 and 34 of rotor 3 still communicate with chambers 62a and 62b of mechanism 60 respectively by corresponding communication passages 31 and 32 and grooves 29 and 30 through fuel passages 68 and 69.
  • rollers 44 of rotor 3 respectively ride over cam ridges of cam surface 41, and hence plungers 42 are urged inwardly along the radial direction of rotor 3, thereby pressurizing the fuel in pump chamber 43a and passage 34.
  • passage 34 since passage 34 communicates with chamber 62b, the fuel in chamber 62b is also pressurized.
  • the high-pressure fuel in chamber 62b urges piston 63 in a direction to reduce the volume of chamber 62a. Therefore, the fuel in the passage between chamber 62a and passage 33 is pressurized to obtain high pressure. Thereafter, when port 50a communicates with one of delivery holes 51 as rotor 3 rotates, the high-pressure fuel in the passage between chamber 62a and passage 33 is delivered from hole 51 connected to port 50a through this port 50a and then injected to the combustion chamber of the engine through delivery passage 52 and delivery valve 53.
  • the fuel is drawn into chambers 62a and 62b of mechanism 60 and then pressurized, so that the fuel in the passage between chamber 62a and passage 33 is distributed and supplied to each combustion chamber of the engine.
  • Rod 65 has the shape described above, and rod 65 can be rotated about its axis by motion of governor sleeve 16 in accordance with the rotational frequency of the engine and can be displaced along its axis by shaft 91 which is rotated in accordance with a depressed amount of the accelerator pedal. Therefore, since rod 65 is moved axially in accordance with the driving condition of the engine and is rotated about its axis, the initial position of piston 63 can be controlled in accordance with the driving condition of the engine by an action of surface 66 of rod 65. Thus, the injection quantity of fuel can be controlled in accordance with the driving condition of the engine because the stroke of piston 63 can be adjusted.
  • cam ring 40 is coupled to piston 46 through pin 45, when the fuel, the pressure of which is controlled in accordance with the driving condition of the engine, is introduced in the working chamber of timer cylinder 47, piston 46 can be moved by the pressure of fuel to displace the rotational position of cam ring 40. Therefore, the cam ridges of cam surface 41 are changed along the circumferential direction of ring 40, and hence the timing of the pump action by reciprocation of plungers 42 is either advanced or delayed. For this reason, the timing of fuel pressurization in passage 34 is controlled, i.e., the timing of fuel pressurization in chamber 62b is controlled, so that the timing of fuel injection is controlled.
  • the injection quantity of fuel can be controlled with high accuracy by adjusting the stroke of piston 63.
  • shuttle mechanism 60 obtained by disposing shuttle cylinder 61 in distribution head 5 along a direction perpendicular to the axis of rotor 3.
  • the present invention is not limited to such mechanism 60.
  • FIGS. 8 to 10 a second embodiment of the present invention is shown.
  • Mechanism 60 of the second embodiment is provided in head cylinder 6, and cylinder 61 of mechanism 60 is disposed parallel to the axis of rotor 3. Since the other structure of the second embodiment is the same as that of the first embodiment, the same parts are denoted by the same reference numerals and a description thereof will be omitted.
  • means for mcving control rod 65 along its axis and displacing it about its axis is not limited to the one including governor sleeve 16 and full load shaft 91 which is rotated in accordance with the depressed amount of the accelerator pedal, but a hydraulic or electromagnetic governor may be used to operate rod 65 in accordance with the driving condition of the engine.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
US07/010,845 1986-02-06 1987-02-04 Distributor type fuel injection pump Expired - Fee Related US4725209A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP61-24515 1986-02-06
JP61024515A JPH0658100B2 (ja) 1986-02-06 1986-02-06 分配型燃料噴射ポンプ

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US4725209A true US4725209A (en) 1988-02-16

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US07/010,845 Expired - Fee Related US4725209A (en) 1986-02-06 1987-02-04 Distributor type fuel injection pump

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US (1) US4725209A (de)
EP (1) EP0232852B1 (de)
JP (1) JPH0658100B2 (de)
DE (1) DE3761687D1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4879984A (en) * 1988-02-10 1989-11-14 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US4915592A (en) * 1987-08-10 1990-04-10 Nippondenso Co., Ltd. Inner-cam type distribution fuel injection pump
US4920940A (en) * 1988-01-16 1990-05-01 Lucas Industries Public Limited Company Fuel pumping apparatus
US4926824A (en) * 1988-05-11 1990-05-22 Volkswagen Ag Fuel injection system
US4940036A (en) * 1987-06-13 1990-07-10 Robert Bosch Gmbh Fuel injection pump

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB870383A (en) * 1957-06-12 1961-06-14 Pierre Etienne Bessiere Improvements in reciprocating piston pumps, in particular for the injection of fuel
US3035523A (en) * 1959-12-31 1962-05-22 Cav Ltd Variable delivery pumps
US3099219A (en) * 1958-05-19 1963-07-30 Bessiere Pierre Etienne Self-regulating reciprocating piston pumps, in particular for the injection of fuel into internal combustion engines
US3101079A (en) * 1961-04-17 1963-08-20 Cav Ltd Liquid fuel pumps for internal combustion engines
GB972446A (en) * 1962-06-27 1964-10-14 Simmonds Precision Products Liquid-fuel distributing means for internal combustion engines
GB2078871A (en) * 1980-06-17 1982-01-13 Hitachi Ltd High pressure fuel injection pump for diesel engine
JPS5835260A (ja) * 1981-08-28 1983-03-01 Hitachi Ltd 分配型燃料噴射ポンプ
US4445822A (en) * 1980-09-22 1984-05-01 Hitachi, Ltd. Injection pump
US4458649A (en) * 1981-03-11 1984-07-10 Hitachi, Ltd. Fuel injection pump for internal combustion engines
US4492200A (en) * 1982-05-14 1985-01-08 Hitachi, Ltd. Fuel pumping apparatus
US4517946A (en) * 1982-02-17 1985-05-21 Yoshiya Takano Fuel injection pump

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB870383A (en) * 1957-06-12 1961-06-14 Pierre Etienne Bessiere Improvements in reciprocating piston pumps, in particular for the injection of fuel
US3099219A (en) * 1958-05-19 1963-07-30 Bessiere Pierre Etienne Self-regulating reciprocating piston pumps, in particular for the injection of fuel into internal combustion engines
US3035523A (en) * 1959-12-31 1962-05-22 Cav Ltd Variable delivery pumps
US3101079A (en) * 1961-04-17 1963-08-20 Cav Ltd Liquid fuel pumps for internal combustion engines
GB972446A (en) * 1962-06-27 1964-10-14 Simmonds Precision Products Liquid-fuel distributing means for internal combustion engines
GB2078871A (en) * 1980-06-17 1982-01-13 Hitachi Ltd High pressure fuel injection pump for diesel engine
US4445822A (en) * 1980-09-22 1984-05-01 Hitachi, Ltd. Injection pump
US4458649A (en) * 1981-03-11 1984-07-10 Hitachi, Ltd. Fuel injection pump for internal combustion engines
JPS5835260A (ja) * 1981-08-28 1983-03-01 Hitachi Ltd 分配型燃料噴射ポンプ
US4450813A (en) * 1981-08-28 1984-05-29 Hitachi, Ltd. Distribution type fuel injection pump
US4517946A (en) * 1982-02-17 1985-05-21 Yoshiya Takano Fuel injection pump
US4492200A (en) * 1982-05-14 1985-01-08 Hitachi, Ltd. Fuel pumping apparatus

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4940036A (en) * 1987-06-13 1990-07-10 Robert Bosch Gmbh Fuel injection pump
US4915592A (en) * 1987-08-10 1990-04-10 Nippondenso Co., Ltd. Inner-cam type distribution fuel injection pump
US4920940A (en) * 1988-01-16 1990-05-01 Lucas Industries Public Limited Company Fuel pumping apparatus
US4879984A (en) * 1988-02-10 1989-11-14 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US4926824A (en) * 1988-05-11 1990-05-22 Volkswagen Ag Fuel injection system

Also Published As

Publication number Publication date
EP0232852A1 (de) 1987-08-19
DE3761687D1 (de) 1990-03-15
EP0232852B1 (de) 1990-02-07
JPH0658100B2 (ja) 1994-08-03
JPS62182471A (ja) 1987-08-10

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